JP6206574B2

JP6206574B2 - Rotary compressor

Info

Publication number: JP6206574B2
Application number: JP2016217601A
Authority: JP
Inventors: 尚哉両角; 卓森下; 基信古川; 大輝片山; 田中　順也; 順也田中
Original assignee: Fujitsu General Ltd
Current assignee: Fujitsu General Ltd
Priority date: 2015-10-30
Filing date: 2016-11-07
Publication date: 2017-10-04
Anticipated expiration: 2035-12-01
Also published as: JP2017082753A; JP6149973B2; JP6128194B2; JP2017089648A; JP2017082756A

Description

本発明は、空気調和機に使用される２シリンダ式のロータリ圧縮機に関する。 The present invention relates to a two-cylinder rotary compressor used in an air conditioner.

例えば、特許文献１には、２シリンダ式のロータリ圧縮機において、下シリンダで圧縮され下吐出孔から吐出する高温の圧縮冷媒が、下端板カバー室（下マフラー室）から上端板カバー室（上マフラー室）に向かって流れる冷媒通路孔を、下シリンダ及び上シリンダの吸入室側から離れた位置に配置することにより、圧縮冷媒が、下シリンダ及び上シリンダの吸入室側の吸入冷媒を加熱するのを抑制し、圧縮機効率を向上させる技術が記載されている。 For example, in Patent Document 1, in a two-cylinder rotary compressor, high-temperature compressed refrigerant that is compressed by a lower cylinder and discharged from a lower discharge hole is transferred from a lower end plate cover chamber (lower muffler chamber) to an upper end plate cover chamber (upper By arranging the refrigerant passage hole flowing toward the muffler chamber) at a position away from the suction chamber side of the lower cylinder and the upper cylinder, the compressed refrigerant heats the suction refrigerant on the suction chamber side of the lower cylinder and the upper cylinder. The technique which suppresses this and improves compressor efficiency is described.

また、特許文献２には、下シリンダで圧縮され下吐出孔から吐出する高温の圧縮冷媒が、下端板を加熱して下シリンダの吸入室内の吸入冷媒を加熱するのを抑制し、圧縮機効率を向上させる技術が記載されている。 Further, in Patent Document 2, high-temperature compressed refrigerant that is compressed in the lower cylinder and discharged from the lower discharge hole suppresses heating of the refrigerant drawn in the suction chamber of the lower cylinder by heating the lower end plate. Techniques for improving the performance are described.

特開２０１４−１４５３１８号公報JP 2014-145318 A 国際公開第２０１３／０９４１１４号International Publication No. 2013/094114

特許文献１に記載されたロータリ圧縮機は、下端板カバー（下マフラーカバー）を膨らませることにより、下端板と下端板カバーとの間に形成される下端板カバー室が大きな容積となっているため、上シリンダで圧縮されて上吐出孔から吐出され冷媒通路孔を逆流して下マフラー室に流れ込む冷媒の量が大きい。 In the rotary compressor described in Patent Document 1, the lower end plate cover chamber formed between the lower end plate and the lower end plate cover has a large volume by inflating the lower end plate cover (lower muffler cover). Therefore, the amount of the refrigerant that is compressed by the upper cylinder, discharged from the upper discharge hole, flows backward through the refrigerant passage hole, and flows into the lower muffler chamber is large.

特許文献２に記載されたロータリ圧縮機は、下端板に設けられた下吐出孔に対して冷媒通路孔が下吐出弁収容部の反対側に配置され、下吐出孔から吐出された冷媒が下吐出弁収容部を通って冷媒通路孔に流れるので、下吐出弁収容部を深くする必要がある。そのため、下端板カバー室（冷媒吐出空間）の容積が大きくなり、上シリンダで圧縮されて上吐出孔から吐出され冷媒通路孔を逆流して下マフラー室に流れ込む冷媒の量が大きい。 In the rotary compressor described in Patent Document 2, the refrigerant passage hole is disposed on the opposite side of the lower discharge valve housing portion with respect to the lower discharge hole provided in the lower end plate, and the refrigerant discharged from the lower discharge hole is lowered. Since it flows into the refrigerant passage hole through the discharge valve accommodating portion, it is necessary to deepen the lower discharge valve accommodating portion. Therefore, the volume of the lower end plate cover chamber (refrigerant discharge space) is increased, and the amount of refrigerant compressed by the upper cylinder and discharged from the upper discharge hole and flowing backward through the refrigerant passage hole and flowing into the lower muffler chamber is large.

以下に、上述の冷媒の逆流現象について説明する。２シリンダ式のロータリ圧縮機では、回転軸の１回転あたりのトルクの変動をできるだけ小さくするため、一般に、吸入、圧縮、吐出の工程が２つのシリンダで１８０°異なる位相で行われるようにされている。起動時など特異な運転条件を除き、通常の室外温度及び室内温度での空気調和機の運転では、１つのシリンダの吐出工程は、１回転中の約１／３である。したがって、１回転中の１／３は、一方のシリンダの吐出工程（吐出弁が開いている工程）、他の１／３は、他方のシリンダの吐出工程、残りの１／３は、両方の吐出弁が閉じている工程である。 Hereinafter, the backflow phenomenon of the refrigerant will be described. In a two-cylinder rotary compressor, in order to minimize the torque fluctuation per rotation of the rotating shaft as much as possible, in general, the steps of suction, compression, and discharge are performed by two cylinders with phases different by 180 °. Yes. Except for special operating conditions such as when starting up, in the operation of the air conditioner at normal outdoor temperature and indoor temperature, the discharge process of one cylinder is about 1/3 during one rotation. Therefore, 1/3 in one rotation is the discharge process of one cylinder (process in which the discharge valve is opened), the other 1/3 is the discharge process of the other cylinder, and the remaining 1/3 is both This is a process in which the discharge valve is closed.

ここで、２つのシリンダの両方の吐出弁が閉じて圧縮室から吐出される冷媒の流れがないときは、上端板カバー室も下端板カバー室も上端板カバー室の外側の圧縮機筐体内と同じ圧力となる。一方のシリンダの吐出工程では、圧縮された高圧域のなかでも冷媒の流れの最も上流となる圧縮室の圧力が最も高く、次いで上端板カバー室、上端板カバー室の外側の圧縮機筐体内の順となる。したがって、上シリンダの吐出弁が開いた直後は、上端板カバー室の外側の圧縮機筐体内や下端板カバー室の圧力よりも上端板カバー室の圧力が高くなる。よって、次の瞬間には、上端板カバー室から上端板カバー室の外側の圧縮機筐体内及び冷媒通路孔を逆流して下マフラー室への冷媒の流れが生じる。 Here, when both the discharge valves of the two cylinders are closed and there is no flow of refrigerant discharged from the compression chamber, the upper end plate cover chamber, the lower end plate cover chamber, the inside of the compressor casing outside the upper end plate cover chamber, Same pressure. In the discharge process of one of the cylinders, the pressure in the compression chamber that is the most upstream in the flow of the refrigerant is the highest in the compressed high pressure region, and then the upper end plate cover chamber and the compressor casing outside the upper end plate cover chamber In order. Therefore, immediately after the discharge valve of the upper cylinder is opened, the pressure in the upper end plate cover chamber becomes higher than the pressure in the compressor casing outside the upper end plate cover chamber and in the lower end plate cover chamber. Therefore, at the next moment, the refrigerant flows into the lower muffler chamber by flowing backward from the upper end plate cover chamber into the compressor casing and the refrigerant passage hole outside the upper end plate cover chamber.

上端板カバー室から上端板カバー室の外側の圧縮機筐体内への冷媒の流れは、本来の流れであるが、上端板カバー室から下端板カバー室へ流れた冷媒は、上シリンダの吐出工程の終了後に再度冷媒通路孔及び上端板カバー室を通って上端板カバー室の外側の圧縮機筐体内に流れることになり、本来、必要のない流れであり、エネルギー損失となってロータリ圧縮機の効率を低下させる、という問題がある。 The flow of the refrigerant from the upper end plate cover chamber into the compressor casing outside the upper end plate cover chamber is the original flow, but the refrigerant flowing from the upper end plate cover chamber to the lower end plate cover chamber is discharged from the upper cylinder. After the end of the process, the refrigerant flows again through the refrigerant passage hole and the upper end plate cover chamber and into the compressor casing outside the upper end plate cover chamber. There is a problem of reducing efficiency.

また、特許文献２に記載されたロータリ圧縮機は、下シリンダで圧縮された冷媒によって下シリンダの下面を覆う下端板が加熱されるのを抑制している。しかしながら、ロータリ圧縮機は、特に、外気が低温の雰囲気で長時間停止した状態では、液化した冷媒が圧縮機筐体内部に溜まってしまうことがある。低温での液冷媒の密度は潤滑油の密度より大きいため、液冷媒は圧縮機筐体内部の最下部に溜まる。この状態でロータリ圧縮機を起動すると、回転軸下端から給油羽根によって液冷媒が吸い上げられる。液冷媒を吸い上げると、液冷媒の粘度は潤滑油の粘度に比較して小さいため、圧縮部の摺動部が潤滑不良となり損傷してしまう恐れがある。 Moreover, the rotary compressor described in patent document 2 is suppressing that the lower end plate which covers the lower surface of a lower cylinder with the refrigerant | coolant compressed with the lower cylinder is heated. However, in the rotary compressor, particularly when the outside air has been stopped for a long time in a low temperature atmosphere, the liquefied refrigerant may accumulate in the compressor housing. Since the density of the liquid refrigerant at a low temperature is larger than the density of the lubricating oil, the liquid refrigerant accumulates at the lowermost part inside the compressor housing. When the rotary compressor is started in this state, the liquid refrigerant is sucked up by the oil supply blades from the lower end of the rotating shaft. If the liquid refrigerant is sucked up, the viscosity of the liquid refrigerant is smaller than the viscosity of the lubricating oil, so that the sliding part of the compression part may be poorly lubricated and damaged.

したがって、ロータリ圧縮機の起動時には、速やかに液冷媒を加熱して気化させる必要があるが、特許文献２に記載されたロータリ圧縮機のように、下端板を加熱することを抑制すると、圧縮機筐体下部に溜まった液冷媒の加熱による気化を抑制することとなり、給油羽根により液冷媒を吸い上げて、圧縮部の潤滑不良による損傷が発生することが問題となる。 Therefore, at the time of starting the rotary compressor, it is necessary to quickly heat and vaporize the liquid refrigerant. However, if the heating of the lower end plate is suppressed as in the rotary compressor described in Patent Document 2, the compressor Vaporization due to heating of the liquid refrigerant accumulated in the lower part of the housing is suppressed, and the problem is that the liquid refrigerant is sucked up by the oil supply blades and damage due to poor lubrication of the compression unit occurs.

また、ロータリ圧縮機では、圧縮機筐体の内部で一部の潤滑油が冷媒に巻き込まれて圧縮機筐体外に吐出され、吐出された潤滑油は、空気調和機の冷媒回路（冷凍サイクル）を一巡して吸入冷媒とともに下シリンダ及び上シリンダに吸入される。下シリンダに吸入された潤滑油は、冷媒とともに下吐出孔から下端板カバー室に吐出される。下端板カバー室に吐出された潤滑油が下端板カバー室内に溜り、下吐出孔が潤滑油に浸漬すると、冷媒の吐出抵抗となり、効率が低下したり騒音が発生するという問題が発生する。この問題は、下端板カバー室の容積が小さくなるほど発生しやすい。 Further, in the rotary compressor, a part of the lubricating oil is caught in the refrigerant inside the compressor casing and discharged out of the compressor casing, and the discharged lubricating oil is the refrigerant circuit (refrigeration cycle) of the air conditioner. Is taken into the lower cylinder and the upper cylinder together with the suction refrigerant. The lubricating oil sucked into the lower cylinder is discharged together with the refrigerant from the lower discharge hole into the lower end plate cover chamber. When the lubricating oil discharged into the lower end plate cover chamber accumulates in the lower end plate cover chamber and the lower discharge hole is immersed in the lubricating oil, there arises a problem that the discharge resistance of the refrigerant becomes low and the efficiency is reduced and noise is generated. This problem tends to occur as the volume of the lower end plate cover chamber decreases.

本発明は、上シリンダで圧縮された冷媒が、冷媒通路孔を逆流するのを抑制して、ロータリ圧縮機の効率低下を防ぐことを目的とする。 An object of the present invention is to prevent the refrigerant compressed by the upper cylinder from flowing back through the refrigerant passage hole, thereby preventing a reduction in the efficiency of the rotary compressor.

本発明は、上部に冷媒を吐出する吐出管が設けられ側面下部に冷媒を吸入する上吸入管及び下吸入管が設けられ密閉された縦置き円筒状の圧縮機筐体と、前記圧縮機筐体の側部に固定され前記上吸入管及び下吸入管に接続するアキュムレータと、前記圧縮機筐体内に配置されるモータと、前記圧縮機筐体内の前記モータの下方に配置され前記モータに駆動され前記上吸入管及び下吸入管を介して前記アキュムレータから冷媒を吸入し圧縮して前記吐出管から吐出する圧縮部と、を有し、前記圧縮部は、環状の上シリンダ及び下シリンダと、前記上シリンダの上側を閉塞する上端板及び前記下シリンダの下側を閉塞する下端板と、前記上シリンダと前記下シリンダの間に配置され前記上シリンダの下側及び前記下シリンダの上側を閉塞する中間仕切板と、前記上端板に設けられた主軸受部と前記下端板に設けられた副軸受部とに支持され前記モータにより回転される回転軸と、前記回転軸に互いに１８０°の位相差をつけて設けられた上偏心部及び下偏心部と、前記上偏心部に嵌合され前記上シリンダの内周面に沿って公転し前記上シリンダ内に上シリンダ室を形成する上ピストンと、前記下偏心部に嵌合され前記下シリンダの内周面に沿って公転し前記下シリンダ内に下シリンダ室を形成する下ピストンと、前記上シリンダに設けられた上ベーン溝から前記上シリンダ室内に突出し前記上ピストンと当接して前記上シリンダ室を上吸入室と上圧縮室に区画する上ベーンと、前記下シリンダに設けられた下ベーン溝から前記下シリンダ室内に突出し前記下ピストンと当接して前記下シリンダ室を下吸入室と下圧縮室に区画する下ベーンと、前記上端板を覆って前記上端板との間に上端板カバー室を形成し前記上端板カバー室と前記圧縮機筐体の内部とを連通する上端板カバー吐出孔を有する上端板カバーと、前記下端板を覆って前記下端板との間に下端板カバー室を形成する下端板カバーと、前記上端板に設けられ前記上圧縮室と前記上端板カバー室とを連通させる上吐出孔と、前記下端板に設けられ前記下圧縮室と前記下端板カバー室とを連通させる下吐出孔と、前記下端板、前記下シリンダ、前記中間仕切板、前記上端板及び前記上シリンダを貫通し前記下端板カバー室と前記上端板カバー室とを連通する冷媒通路孔と、を備えるロータリ圧縮機において、前記上端板に設けられ前記上吐出孔の位置から溝状に延びる上吐出弁収容凹部と、前記下端板に設けられ前記下吐出孔の位置から溝状に延びる下吐出弁収容凹部と、後端部が前記上吐出弁収容凹部内に上リベットにより固定され前部が前記上吐出孔を開閉するリード弁型の上吐出弁及び後端部が該上吐出弁に重ねられて前記上吐出弁収容凹部内に前記上リベットにより固定され前部が反っていて前記上吐出弁の開度を規制する上吐出弁押さえと、後端部が前記下吐出弁収容凹部内に下リベットにより固定され前部が前記下吐出孔を開閉するリード弁型の下吐出弁及び後端部が該下吐出弁に重ねられて前記下吐出弁収容凹部内に前記下リベットにより固定され前部が反っていて前記下吐出弁の開度を規制し前記下吐出弁収容凹部内に収容される下吐出弁押さえと、を備え、前記下端板カバーは平板状に形成され、前記下端板には、前記下吐出弁収容凹部の前記下吐出孔側に重なるように下吐出室凹部が形成され、該下吐出室凹部は、前記副軸受部の中心と、前記下吐出孔の中心と前記下リベットの中心を結ぶ線分の中点と、を通る第１径線と、前記副軸受部の中心を中心として前記下吐出孔の方向へピッチ角９０°開いた第２径線との間の扇形の範囲内に形成され、前記下端板カバー室は、前記下吐出室凹部と前記下吐出弁収容凹部とにより構成され、前記冷媒通路孔は、前記下吐出孔に対して前記下端板の外周側の位置、かつ、前記下吐出室凹部の内周壁の内側に、前記下吐出室凹部と連通して配置されたことを特徴とする。 The present invention provides a vertically mounted cylindrical compressor housing which is provided with an upper suction pipe and a lower suction pipe which are provided with a discharge pipe for discharging a refrigerant at the upper part and with which a refrigerant is sucked at a lower part of the side surface, and the compressor casing. An accumulator fixed to the side of the body and connected to the upper suction pipe and the lower suction pipe, a motor disposed in the compressor housing, and disposed below the motor in the compressor housing and driven by the motor And a compression part that sucks and compresses the refrigerant from the accumulator through the upper suction pipe and the lower suction pipe and discharges the refrigerant from the discharge pipe, and the compression part includes an annular upper cylinder and a lower cylinder, An upper end plate for closing the upper side of the upper cylinder, a lower end plate for closing the lower side of the lower cylinder, and a lower side of the upper cylinder and the upper side of the lower cylinder, which are disposed between the upper cylinder and the lower cylinder. Intermediate A rotating shaft supported by a cutting plate, a main bearing portion provided on the upper end plate, and a sub bearing portion provided on the lower end plate and rotated by the motor, and a phase difference of 180 ° between the rotating shaft and each other. An upper eccentric portion and a lower eccentric portion provided on the upper piston, an upper piston fitted into the upper eccentric portion and revolved along an inner peripheral surface of the upper cylinder to form an upper cylinder chamber in the upper cylinder, A lower piston fitted into the lower eccentric part and revolves along the inner peripheral surface of the lower cylinder to form a lower cylinder chamber in the lower cylinder, and an upper vane groove provided in the upper cylinder into the upper cylinder chamber An upper vane that protrudes into contact with the upper piston and divides the upper cylinder chamber into an upper suction chamber and an upper compression chamber, and protrudes into the lower cylinder chamber from a lower vane groove provided in the lower cylinder and contacts the lower piston. The lower siri An upper end plate cover chamber is formed between the lower vane that divides the chamber into a lower suction chamber and a lower compression chamber, and the upper end plate so as to cover the upper end plate, and the interior of the upper end plate cover chamber and the compressor housing An upper end plate cover having an upper end plate cover discharge hole communicating therewith, a lower end plate cover that covers the lower end plate and forms a lower end plate cover chamber between the lower end plate, and the upper compression provided in the upper end plate An upper discharge hole for communicating the chamber and the upper end plate cover chamber, a lower discharge hole provided in the lower end plate for communicating the lower compression chamber and the lower end plate cover chamber, the lower end plate, the lower cylinder, In the rotary compressor provided with an intermediate partition plate, the upper end plate, and the upper cylinder, and a refrigerant passage hole communicating with the lower end plate cover chamber and the upper end plate cover chamber, the upper discharge provided in the upper end plate Upper spout extending in the shape of a groove from the position of the hole A valve receiving recess, a lower discharge valve receiving recess provided in the lower end plate and extending in a groove shape from the position of the lower discharge hole, a rear end portion fixed by an upper rivet in the upper discharge valve receiving recess, and a front portion A reed valve type upper discharge valve that opens and closes the upper discharge hole and a rear end portion are overlapped with the upper discharge valve, fixed in the upper discharge valve housing recess by the upper rivet, and a front portion is warped, and the upper discharge valve An upper discharge valve presser that regulates the degree of opening, and a reed valve type lower discharge valve and a rear end portion whose rear end portion is fixed by a lower rivet in the lower discharge valve housing recess and whose front portion opens and closes the lower discharge hole Is overlapped with the lower discharge valve and fixed in the lower discharge valve housing recess by the lower rivet, and the front part is warped to regulate the opening of the lower discharge valve and accommodated in the lower discharge valve housing recess. A lower discharge valve presser, and the lower end plate cover is formed in a flat plate shape. A lower discharge chamber recess is formed in the lower end plate so as to overlap the lower discharge hole side of the lower discharge valve housing recess, and the lower discharge chamber recess has a center of the auxiliary bearing portion and the lower discharge hole. A first diameter line passing through the center of the line segment connecting the center of the lower rivet and the second diameter opened at a pitch angle of 90 ° in the direction of the lower discharge hole with the center of the auxiliary bearing portion as the center The lower end plate cover chamber is formed by the lower discharge chamber recess and the lower discharge valve housing recess, and the refrigerant passage hole is formed with respect to the lower discharge hole. The lower discharge plate is disposed on the outer peripheral side of the lower end plate and inside the inner peripheral wall of the lower discharge chamber recess so as to communicate with the lower discharge chamber recess.

本発明は、下シリンダで圧縮された冷媒が、冷媒通路孔を逆流するのを抑制して、ロータリ圧縮機の効率低下を防ぐことができる。 The present invention can prevent the refrigerant compressed by the lower cylinder from flowing backward through the refrigerant passage hole and prevent a reduction in the efficiency of the rotary compressor.

図１は、本発明に係るロータリ圧縮機の実施例１を示す縦断面図である。FIG. 1 is a longitudinal sectional view showing a first embodiment of a rotary compressor according to the present invention. 図２は、実施例１のロータリ圧縮機の圧縮部を示す上方分解斜視図である。FIG. 2 is an upper exploded perspective view illustrating a compression unit of the rotary compressor according to the first embodiment. 図３は、実施例１のロータリ圧縮機の回転軸と給油羽根を示す上方分解斜視図である。FIG. 3 is an upper exploded perspective view showing the rotating shaft and the oil supply blades of the rotary compressor of the first embodiment. 図４は、実施例１のロータリ圧縮機の下端板を示す下面図である。FIG. 4 is a bottom view showing a lower end plate of the rotary compressor of the first embodiment. 図５は、実施例１のロータリ圧縮機の下吐出弁を取付けた下吐出弁収容凹部を示す縦断面図である。FIG. 5 is a longitudinal cross-sectional view showing a lower discharge valve accommodating recess to which the lower discharge valve of the rotary compressor of the first embodiment is attached. 図６は、実施例２のロータリ圧縮機の下吐出弁を取付けた下吐出弁収容凹部を示す縦断面図である。FIG. 6 is a longitudinal cross-sectional view showing a lower discharge valve housing recess in which the lower discharge valve of the rotary compressor of the second embodiment is attached. 図７は、実施例３のロータリ圧縮機の下吐出弁を取付けた下吐出弁収容凹部を示す縦断面図である。FIG. 7 is a longitudinal cross-sectional view showing a lower discharge valve accommodating recess to which a lower discharge valve of the rotary compressor of the third embodiment is attached. 図８は、実施例４のロータリ圧縮機の下端板を示す下面図である。FIG. 8 is a bottom view showing a lower end plate of the rotary compressor of the fourth embodiment. 図９は、実施例５のロータリ圧縮機の下端板を示す下面図である。FIG. 9 is a bottom view of the lower end plate of the rotary compressor of the fifth embodiment. 図１０は、実施例６のロータリ圧縮機の下端板を示す下方斜視図である。FIG. 10 is a lower perspective view illustrating the lower end plate of the rotary compressor of the sixth embodiment. 図１１は、実施例７のロータリ圧縮機の下端板と下端板カバーとを重ねた状態を示す下面図である。FIG. 11 is a bottom view illustrating a state in which the lower end plate and the lower end plate cover of the rotary compressor according to the seventh embodiment are overlapped.

以下に、本発明を実施するための形態（実施例）につき、図面を参照しつつ詳細に説明する。 EMBODIMENT OF THE INVENTION Below, the form (Example) for implementing this invention is demonstrated in detail, referring drawings.

図１は、本発明に係るロータリ圧縮機の実施例１を示す縦断面図であり、図２は、実施例１のロータリ圧縮機の圧縮部を示す上方分解斜視図であり、図３は、実施例１のロータリ圧縮機の回転軸と給油羽根を示す上方分解斜視図である。 1 is a longitudinal sectional view showing Embodiment 1 of a rotary compressor according to the present invention, FIG. 2 is an upper exploded perspective view showing a compression section of the rotary compressor of Embodiment 1, and FIG. FIG. 3 is an exploded top perspective view showing a rotation shaft and oil supply blades of the rotary compressor according to the first embodiment.

図１に示すように、ロータリ圧縮機１は、密閉された縦置き円筒状の圧縮機筐体１０内の下部に配置された圧縮部１２と、圧縮部１２の上方に配置され、回転軸１５を介して圧縮部１２を駆動するモータ１１と、圧縮機筐体１０の側部に固定された縦置き円筒状のアキュムレータ２５と、を備えている。 As shown in FIG. 1, the rotary compressor 1 includes a compression unit 12 disposed at a lower portion in a sealed vertical cylindrical compressor housing 10, a compression unit 12 disposed above the compression unit 12, and a rotating shaft 15. A motor 11 that drives the compression unit 12 through the vertical axis, and a vertical cylindrical accumulator 25 that is fixed to a side portion of the compressor housing 10.

アキュムレータ２５は、上吸入管１０５及びアキュムレータ上Ｌ字管３１Ｔを介して上シリンダ１２１Ｔの上吸入室１３１Ｔ（図２参照）と接続し、下吸入管１０４及びアキュムレータ下Ｌ字管３１Ｓを介して下シリンダ１２１Ｓの下吸入室１３１Ｓ（図２参照）と接続している。 The accumulator 25 is connected to the upper suction chamber 131T (see FIG. 2) of the upper cylinder 121T via the upper suction pipe 105 and the accumulator upper L-shaped pipe 31T, and is connected to the lower side via the lower suction pipe 104 and the lower L-shaped pipe 31S of the accumulator. The cylinder 121S is connected to the lower suction chamber 131S (see FIG. 2).

モータ１１は、外側にステータ１１１を、内側にロータ１１２を備え、ステータ１１１は、圧縮機筐体１０の内周面に焼嵌め固定され、ロータ１１２は、回転軸１５に焼嵌めにより固定されている。 The motor 11 includes a stator 111 on the outer side and a rotor 112 on the inner side. The stator 111 is shrink-fitted and fixed to the inner peripheral surface of the compressor housing 10, and the rotor 112 is fixed to the rotary shaft 15 by shrink-fitting. Yes.

回転軸１５は、下偏心部１５２Ｓの下方の副軸部１５１が下端板１６０Ｓに設けられた副軸受部１６１Ｓに回転自在に嵌合して支持され、上偏心部１５２Ｔの上方の主軸部１５３が上端板１６０Ｔに設けられた主軸受部１６１Ｔに回転自在に嵌合して支持され、互いに１８０度の位相差をつけて設けられた上偏心部１５２Ｔ及び下偏心部１５２Ｓがそれぞれ上ピストン１２５Ｔ及び下ピストン１２５Ｓに回転自在に嵌合することによって、圧縮部１２全体に対して回転自在に支持されるとともに、回転によって上ピストン１２５Ｔ及び下ピストン１２５Ｓをそれぞれ上シリンダ１２１Ｔ、下シリンダ１２１Ｓの内周面に沿って公転運動させる。 The rotary shaft 15 is supported by a secondary shaft portion 151 below the lower eccentric portion 152S being rotatably fitted to a secondary bearing portion 161S provided on the lower end plate 160S, and a main shaft portion 153 above the upper eccentric portion 152T. An upper eccentric portion 152T and a lower eccentric portion 152S, which are rotatably fitted to and supported by a main bearing portion 161T provided on the upper end plate 160T and are provided with a phase difference of 180 degrees from each other, are respectively provided with an upper piston 125T and a lower By being rotatably fitted to the piston 125S, the entire compression portion 12 is rotatably supported, and the upper piston 125T and the lower piston 125S are respectively rotated on the inner peripheral surfaces of the upper cylinder 121T and the lower cylinder 121S. Revolve along.

圧縮機筐体１０内部には、圧縮部１２の摺動部の潤滑と上圧縮室１３３Ｔ（図２参照）及び下圧縮室１３３Ｓ（図２参照）のシールのために、潤滑油１８が圧縮部１２をほぼ浸漬する量だけ封入されている。圧縮機筐体１０の下側には、ロータリ圧縮機１全体を支持する複数の弾性支持部材（図示せず）を係止する取付脚３１０が固定されている。 Lubricating oil 18 is contained in the compressor housing 10 for lubricating the sliding portion of the compression portion 12 and sealing the upper compression chamber 133T (see FIG. 2) and the lower compression chamber 133S (see FIG. 2). 12 is enclosed in an amount that substantially immerses 12. An attachment leg 310 that fixes a plurality of elastic support members (not shown) that support the entire rotary compressor 1 is fixed to the lower side of the compressor housing 10.

図２に示すように、圧縮部１２は、上からドーム状の膨出部を有する上端板カバー１７０Ｔ、上端板１６０Ｔ、上シリンダ１２１Ｔ、中間仕切板１４０、下シリンダ１２１Ｓ、下端板１６０Ｓ及び平板状の下端板カバー１７０Ｓを積層して構成されている。圧縮部１２全体は、上下から略同心円上に配置された複数の通しボルト１７４，１７５及び補助ボルト１７６によって固定されている。 As shown in FIG. 2, the compression unit 12 includes an upper end plate cover 170T having a dome-shaped bulging portion from above, an upper end plate 160T, an upper cylinder 121T, an intermediate partition plate 140, a lower cylinder 121S, a lower end plate 160S, and a flat plate shape. The lower end plate cover 170S is laminated. The entire compression unit 12 is fixed by a plurality of through bolts 174 and 175 and auxiliary bolts 176 arranged substantially concentrically from above and below.

環状の上シリンダ１２１Ｔには、上吸入管１０５と嵌合する上吸入孔１３５Ｔが設けられている。環状の下シリンダ１２１Ｓには、下吸入管１０４と嵌合する下吸入孔１３５Ｓが設けられている。また、上シリンダ１２１Ｔの上シリンダ室１３０Ｔには、上ピストン１２５Ｔが配置されている。下シリンダ１２１Ｓの下シリンダ室１３０Ｓには、下ピストン１２５Ｓが配置されている。 An annular upper cylinder 121T is provided with an upper suction hole 135T that fits into the upper suction pipe 105. The annular lower cylinder 121S is provided with a lower suction hole 135S that fits into the lower suction pipe 104. An upper piston 125T is disposed in the upper cylinder chamber 130T of the upper cylinder 121T. A lower piston 125S is disposed in the lower cylinder chamber 130S of the lower cylinder 121S.

上シリンダ１２１Ｔには、上シリンダ室１３０Ｔから放射状に外方へ延びる上ベーン溝１２８Ｔが設けられ、上ベーン溝１２８Ｔには上ベーン１２７Ｔが配置されている。下シリンダ１２１Ｓには、下シリンダ室１３０Ｓから放射状に外方へ延びる下ベーン溝１２８Ｓが設けられ、下ベーン溝１２８Ｓには下ベーン１２７Ｓが配置されている。 The upper cylinder 121T is provided with an upper vane groove 128T extending radially outward from the upper cylinder chamber 130T, and an upper vane 127T is disposed in the upper vane groove 128T. The lower cylinder 121S is provided with a lower vane groove 128S extending radially outward from the lower cylinder chamber 130S, and a lower vane 127S is disposed in the lower vane groove 128S.

上シリンダ１２１Ｔには、外側面から上ベーン溝１２８Ｔと重なる位置に上シリンダ室１３０Ｔに貫通しない深さで上スプリング穴１２４Ｔが設けられ、上スプリング穴１２４Ｔには上スプリング１２６Ｔが配置されている。下シリンダ１２１Ｓには、外側面から下ベーン溝１２８Ｓと重なる位置に下シリンダ室１３０Ｓに貫通しない深さで下スプリング穴１２４Ｓが設けられ、下スプリング穴１２４Ｓには下スプリング１２６Ｓが配置されている。 The upper cylinder 121T is provided with an upper spring hole 124T at a position that does not penetrate the upper cylinder chamber 130T at a position overlapping the upper vane groove 128T from the outer surface, and the upper spring 126T is disposed in the upper spring hole 124T. The lower cylinder 121S is provided with a lower spring hole 124S at a position that does not penetrate the lower cylinder chamber 130S at a position overlapping the lower vane groove 128S from the outer surface, and a lower spring 126S is disposed in the lower spring hole 124S.

上シリンダ室１３０Ｔは、上下をそれぞれ上端板１６０Ｔ及び中間仕切板１４０で閉塞されている。下シリンダ室１３０Ｓは、上下をそれぞれ中間仕切板１４０及び下端板１６０Ｓで閉塞されている。 The upper cylinder chamber 130T is closed at the top and bottom by an upper end plate 160T and an intermediate partition plate 140, respectively. The lower cylinder chamber 130S is closed at the top and bottom by an intermediate partition plate 140 and a lower end plate 160S, respectively.

上シリンダ室１３０Ｔは、上ベーン１２７Ｔが上スプリング１２６Ｔに押圧されて上ピストン１２５Ｔの外周面に当接することによって、上吸入孔１３５Ｔに連通する上吸入室１３１Ｔと、上端板１６０Ｔに設けられた上吐出孔１９０Ｔに連通する上圧縮室１３３Ｔと、に区画される。下シリンダ室１３０Ｓは、下ベーン１２７Ｓが下スプリング１２６Ｓに押圧されて下ピストン１２５Ｓの外周面に当接することによって、下吸入孔１３５Ｓに連通する下吸入室１３１Ｓと、下端板１６０Ｓに設けられた下吐出孔１９０Ｓに連通する下圧縮室１３３Ｓと、に区画される。 The upper cylinder chamber 130T includes an upper suction chamber 131T communicating with the upper suction hole 135T and an upper plate 160T provided by the upper vane 127T being pressed by the upper spring 126T and coming into contact with the outer peripheral surface of the upper piston 125T. The upper compression chamber 133T communicated with the discharge hole 190T. The lower cylinder chamber 130S includes a lower suction chamber 131S communicating with the lower suction hole 135S and a lower plate provided in the lower end plate 160S when the lower vane 127S is pressed by the lower spring 126S and comes into contact with the outer peripheral surface of the lower piston 125S. And a lower compression chamber 133S communicating with the discharge hole 190S.

上端板１６０Ｔには、上端板１６０Ｔを貫通して上シリンダ１２１Ｔの上圧縮室１３３Ｔと連通する上吐出孔１９０Ｔが設けられ、上吐出孔１９０Ｔの出口側には、上吐出孔１９０Ｔを囲む環状の上弁座（図示せず）が形成されている。上端板１６０Ｔには、上吐出孔１９０Ｔの位置から上端板１６０Ｔの周方向に溝状に延びる上吐出弁収容凹部１６４Ｔが形成されている。 The upper end plate 160T is provided with an upper discharge hole 190T that penetrates the upper end plate 160T and communicates with the upper compression chamber 133T of the upper cylinder 121T, and an annular shape surrounding the upper discharge hole 190T is provided on the outlet side of the upper discharge hole 190T. An upper valve seat (not shown) is formed. The upper end plate 160T is formed with an upper discharge valve accommodating recess 164T extending in a groove shape from the position of the upper discharge hole 190T in the circumferential direction of the upper end plate 160T.

上吐出弁収容凹部１６４Ｔには、後端部が上吐出弁収容凹部１６４Ｔ内に上リベット２０２Ｔにより固定され前部が上吐出孔１９０Ｔを開閉するリード弁型の上吐出弁２００Ｔ及び後端部が上吐出弁２００Ｔに重ねられて上吐出弁収容凹部１６４Ｔ内に上リベット２０２Ｔにより固定され前部が湾曲して（反って）いて上吐出弁２００Ｔの開度を規制する上吐出弁押さえ２０１Ｔ全体が収容されている。 The upper discharge valve accommodating recess 164T has a reed valve type upper discharge valve 200T and a rear end whose rear end is fixed by an upper rivet 202T in the upper discharge valve accommodating recess 164T and whose front opens and closes the upper discharge hole 190T. The upper discharge valve holder 201T as a whole is placed on the upper discharge valve 200T and fixed in the upper discharge valve housing recess 164T by the upper rivet 202T, and the front part is curved (warped) to regulate the opening degree of the upper discharge valve 200T. Contained.

下端板１６０Ｓには、下端板１６０Ｓを貫通して下シリンダ１２１Ｓの下圧縮室１３３Ｓと連通する下吐出孔１９０Ｓが設けられ、下吐出孔１９０Ｓの出口側には、下吐出孔１９０Ｓを囲む環状の下弁座１９１Ｓ（図４参照）が形成されている。下端板１６０Ｓには、下吐出孔１９０Ｔの位置から下端板１６０Ｓの周方向に溝状に延びる下吐出弁収容凹部１６４Ｓ（図４参照）が形成されている。 The lower end plate 160S is provided with a lower discharge hole 190S that penetrates the lower end plate 160S and communicates with the lower compression chamber 133S of the lower cylinder 121S, and an annular shape surrounding the lower discharge hole 190S is provided on the outlet side of the lower discharge hole 190S. A lower valve seat 191S (see FIG. 4) is formed. The lower end plate 160S is formed with a lower discharge valve accommodating recess 164S (see FIG. 4) extending from the position of the lower discharge hole 190T in a groove shape in the circumferential direction of the lower end plate 160S.

下吐出弁収容凹部１６４Ｓには、後端部が下吐出弁収容凹部１６４Ｓ内に下リベット２０２Ｓにより固定され前部が下吐出孔１９０Ｓを開閉するリード弁型の下吐出弁２００Ｓ及び後端部が下吐出弁２００Ｓに重ねられて下吐出弁収容凹部１６４Ｓ内に下リベット２０２Ｓにより固定され前部が湾曲して（反って）いて下吐出弁２００Ｓの開度を規制する下吐出弁押さえ２０１Ｓの全部が収容されている。 The lower discharge valve accommodating recess 164S has a reed valve type lower discharge valve 200S and a rear end that are fixed by a lower rivet 202S in the lower discharge valve accommodating recess 164S and the front portion opens and closes the lower discharge hole 190S. All of the lower discharge valve presser 201S that overlaps with the lower discharge valve 200S and is fixed in the lower discharge valve housing recess 164S by the lower rivet 202S and the front part is curved (warped) to regulate the opening degree of the lower discharge valve 200S. Is housed.

互いに密着固定された上端板１６０Ｔとドーム状の膨出部を有する上端板カバー１７０Ｔとの間には、上端板カバー室１８０Ｔが形成される。互いに密着固定された下端板１６０Ｓと平板状の下端板カバー１７０Ｓとの間には、下端板カバー室１８０Ｓが形成される（下端板カバー室１８０Ｓの詳細については後述する）。下端板１６０Ｓ、下シリンダ１２１Ｓ、中間仕切板１４０、上端板１６０Ｔ及び上シリンダ１２１Ｔを貫通し下端板カバー室１８０Ｓと上端板カバー室１８０Ｔとを連通する冷媒通路孔１３６が設けられている。 An upper-end plate cover chamber 180T is formed between the upper-end plate 160T and the upper-end plate cover 170T having a dome-shaped bulge. A lower end plate cover chamber 180S is formed between the lower end plate 160S and the flat lower end plate cover 170S that are closely fixed to each other (details of the lower end plate cover chamber 180S will be described later). A refrigerant passage hole 136 that penetrates the lower end plate 160S, the lower cylinder 121S, the intermediate partition plate 140, the upper end plate 160T, and the upper cylinder 121T and communicates the lower end plate cover chamber 180S and the upper end plate cover chamber 180T is provided.

図３に示すように、回転軸１５には、下端から上端まで貫通する給油縦孔１５５が設けられ、給油縦孔１５５には給油羽根１５８が圧入されている。また、回転軸１５の側面には、給油縦孔１５５に連通する複数の給油横孔１５６が設けられている。 As shown in FIG. 3, the rotary shaft 15 is provided with an oil supply vertical hole 155 that penetrates from the lower end to the upper end, and an oil supply blade 158 is press-fitted into the oil supply vertical hole 155. In addition, a plurality of oil supply lateral holes 156 communicating with the oil supply vertical holes 155 are provided on the side surface of the rotating shaft 15.

以下に、回転軸１５の回転による冷媒の流れを説明する。上シリンダ室１３０Ｔ内において、回転軸１５の回転によって、回転軸１５の上偏心部１５２Ｔに嵌合された上ピストン１２５Ｔが、上シリンダ室１３０Ｔの外周面（上シリンダ１２１Ｔの内周面）に沿って公転することにより、上吸入室１３１Ｔが容積を拡大しながら上吸入管１０５から冷媒を吸入し、上圧縮室１３３Ｔが容積を縮小しながら冷媒を圧縮し、圧縮した冷媒の圧力が上吐出弁２００Ｔの外側の上端板カバー室１８０Ｔの圧力より高くなると、上吐出弁２００Ｔが開いて上圧縮室１３３Ｔから上端板カバー室１８０Ｔへ冷媒が吐出される。上端板カバー室１８０Ｔに吐出された冷媒は、上端板カバー１７０Ｔに設けられた上端板カバー吐出孔１７２Ｔ（図１参照）から圧縮機筐体１０内に吐出される。 Below, the flow of the refrigerant | coolant by rotation of the rotating shaft 15 is demonstrated. In the upper cylinder chamber 130T, the upper piston 125T fitted to the upper eccentric portion 152T of the rotary shaft 15 is rotated along the outer peripheral surface of the upper cylinder chamber 130T (the inner peripheral surface of the upper cylinder 121T) by the rotation of the rotary shaft 15. Thus, the upper suction chamber 131T sucks refrigerant from the upper suction pipe 105 while expanding the volume, and the upper compression chamber 133T compresses the refrigerant while reducing the volume, and the pressure of the compressed refrigerant is changed to the upper discharge valve. When the pressure is higher than the pressure in the upper end plate cover chamber 180T outside the 200T, the upper discharge valve 200T is opened and the refrigerant is discharged from the upper compression chamber 133T to the upper end plate cover chamber 180T. The refrigerant discharged into the upper end plate cover chamber 180T is discharged into the compressor housing 10 from an upper end plate cover discharge hole 172T (see FIG. 1) provided in the upper end plate cover 170T.

また、下シリンダ室１３０Ｓ内において、回転軸１５の回転によって、回転軸１５の下偏芯部１５２Ｓに嵌合された下ピストン１２５Ｓが、下シリンダ室１３０Ｓの外周面（下シリンダ１２１Ｓの内周面）に沿って公転することにより、下吸入室１３１Ｓが容積を拡大しながら下吸入管１０４から冷媒を吸入し、下圧縮室１３３Ｓが容積を縮小しながら冷媒を圧縮し、圧縮した冷媒の圧力が下吐出弁２００Ｓの外側の下端板カバー室１８０Ｓの圧力より高くなると、下吐出弁２００Ｓが開いて下圧縮室１３３Ｓから下端板カバー室１８０Ｓへ冷媒が吐出される。下端板カバー室１８０Ｓに吐出された冷媒は、冷媒通路孔１３６及び上端板カバー室１８０Ｔを通って上端板カバー１７０Ｔに設けられた上端板カバー吐出孔１７２Ｔ（図１参照）から圧縮機筐体１０内部に吐出される。 Further, in the lower cylinder chamber 130S, the lower piston 125S fitted to the lower eccentric portion 152S of the rotary shaft 15 by the rotation of the rotary shaft 15 causes the outer peripheral surface of the lower cylinder chamber 130S (the inner peripheral surface of the lower cylinder 121S). ), The lower suction chamber 131S sucks in the refrigerant from the lower suction pipe 104 while increasing the volume, and the lower compression chamber 133S compresses the refrigerant while reducing the volume, and the pressure of the compressed refrigerant is reduced. When the pressure in the lower end plate cover chamber 180S outside the lower discharge valve 200S becomes higher, the lower discharge valve 200S opens and the refrigerant is discharged from the lower compression chamber 133S to the lower end plate cover chamber 180S. The refrigerant discharged into the lower end plate cover chamber 180S passes through the refrigerant passage hole 136 and the upper end plate cover chamber 180T, and passes through the upper end plate cover discharge hole 172T (see FIG. 1) provided in the upper end plate cover 170T. It is discharged inside.

圧縮機筐体１０内に吐出された冷媒は、ステータ１１１外周に設けられた上下を連通する切欠き（図示せず）、又はステータ１１１の巻線部の隙間（図示せず）、又はステータ１１１とロータ１１２との隙間１１５（図１参照）を通ってモータ１１の上方に導かれ、圧縮機筐体１０上部の吐出管１０７から吐出される。 The refrigerant discharged into the compressor housing 10 is a notch (not shown) provided on the outer periphery of the stator 111 that communicates with the upper and lower sides, a gap (not shown) between winding portions of the stator 111, or the stator 111. Is guided to the upper side of the motor 11 through the gap 115 (see FIG. 1) between the rotor 112 and the rotor 112, and is discharged from the discharge pipe 107 at the top of the compressor housing 10.

以下に、潤滑油１８の流れを説明する。潤滑油１８は、回転軸１５の下端から給油縦孔１５５及び複数の給油横孔１５６を通って、副軸受部１６１Ｓと回転軸１５の副軸部１５１との摺動面、主軸受部１６１Ｔと回転軸１５の主軸部１５３との摺動面、回転軸１５の下偏心部１５２Ｓと下ピストン１２５Ｓとの摺動面、上偏心部１５２Ｔと上ピストン１２５Ｔとの摺動面、に給油され、それぞれの摺動面を潤滑する。 Hereinafter, the flow of the lubricating oil 18 will be described. The lubricating oil 18 passes from the lower end of the rotary shaft 15 through the oil supply vertical hole 155 and the plurality of oil supply horizontal holes 156, and slides between the sub bearing portion 161S and the sub shaft portion 151 of the rotary shaft 15, the main bearing portion 161T, Oil is supplied to the sliding surface of the rotating shaft 15 with the main shaft portion 153, the sliding surface of the lower eccentric portion 152S of the rotating shaft 15 and the lower piston 125S, and the sliding surface of the upper eccentric portion 152T and the upper piston 125T, respectively. Lubricate the sliding surface.

給油羽根１５８は、給油縦孔１５５内で潤滑油１８に遠心力を与えることにより潤滑油１８を吸い上げ、潤滑油１８が圧縮機筐体１０内から冷媒とともに排出されて油面が低くなった場合にも、確実に上記の摺動面に潤滑油１８を供給する役目を担っている。 The oil supply blade 158 sucks up the lubricating oil 18 by applying a centrifugal force to the lubricating oil 18 in the oil supply vertical hole 155, and the lubricating oil 18 is discharged from the compressor housing 10 together with the refrigerant to lower the oil level. In addition, the lubricant 18 is surely supplied to the sliding surface.

次に、実施例１のロータリ圧縮機１の特徴的な構成について説明する。図４は、実施例１のロータリ圧縮機の下端板を示す下面図であり、図５は、実施例１のロータリ圧縮機の下吐出弁を取付けた下吐出弁収容凹部を示す縦断面図である。 Next, a characteristic configuration of the rotary compressor 1 according to the first embodiment will be described. FIG. 4 is a bottom view showing a lower end plate of the rotary compressor of the first embodiment, and FIG. 5 is a longitudinal sectional view showing a lower discharge valve housing concave portion to which the lower discharge valve of the rotary compressor of the first embodiment is attached. is there.

図４に示すように、下端板カバー室１８０Ｓは、下端板カバー１７０Ｓが平板状で上端板カバー１７０Ｔのようなドーム状の膨出部を有しないので、下端板１６０Ｓに設けられた下吐出室凹部１６３Ｓと下吐出弁収容凹部１６４Ｓとにより構成される。下吐出弁収容凹部１６４Ｓは、下吐出孔１９０Ｓの位置から、副軸受部１６１Ｓの中心Ｏ_１と下吐出孔１９０Ｓの中心Ｏ_２とを結ぶ径線Ｌ_１と交差する方向、言い替えれば、下端板１６０Ｓの周方向に直線的に溝状に延びている。下吐出弁収容凹部１６４Ｓは、下吐出室凹部１６３Ｓとつながっている。下吐出弁収容凹部１６４Ｓは、その幅が下吐出弁２００Ｓ及び下吐出弁押さえ２０１Ｓの幅よりわずかに大きく形成され、下吐出弁２００Ｓ及び下吐出弁押さえ２０１Ｓを収容するとともに、下吐出弁２００Ｓ及び下吐出弁押さえ２０１Ｓを位置決めしている。 As shown in FIG. 4, the lower end plate cover chamber 180S has a lower discharge plate chamber provided in the lower end plate 160S because the lower end plate cover 170S has a flat plate shape and does not have a dome-like bulge portion like the upper end plate cover 170T. It is comprised by the recessed part 163S and the lower discharge valve accommodation recessed part 164S. Lower discharge valve housing recess 164S from the position of the lower discharge holes 190S, a direction which intersects the radial line _{L 1} connecting the center _{O 2} of the center _{O 1} and the lower discharge holes 190S sub bearing portion 161S, in other words, the lower end plate The groove extends linearly in the circumferential direction of 160S. The lower discharge valve housing recess 164S is connected to the lower discharge chamber recess 163S. The lower discharge valve accommodating recess 164S is formed to have a width slightly larger than the width of the lower discharge valve 200S and the lower discharge valve presser 201S, and accommodates the lower discharge valve 200S and the lower discharge valve presser 201S, and the lower discharge valve 200S and The lower discharge valve holder 201S is positioned.

下吐出室凹部１６３Ｓは、下吐出弁収容凹部１６４Ｓの下吐出孔１９０Ｓ側に重なるように、下吐出弁収容凹部１６４Ｓの深さと同じ深さに形成されている。下吐出弁収容凹部１６４Ｓの下吐出孔１９０Ｓ側は、下吐出室凹部１６３Ｓに収容される。 The lower discharge chamber recess 163S is formed to the same depth as the lower discharge valve storage recess 164S so as to overlap the lower discharge hole 190S side of the lower discharge valve storage recess 164S. The lower discharge hole 190S side of the lower discharge valve housing recess 164S is housed in the lower discharge chamber recess 163S.

下吐出室凹部１６３Ｓは、副軸受部１６１Ｓの中心Ｏ_１と、下吐出孔１９０Ｓの中心Ｏ_２と下リベット２０２Ｓの中心Ｏ_３を結ぶ線分Ｌ_２（長さＦ）の中点Ｏ_４と、を通る径線Ｌ_３と、副軸受部１６１Ｓの中心Ｏ_１を中心として下吐出孔１９０Ｓの方向へピッチ角９０°開いた径線Ｌ_４との間の扇形の範囲内に形成する。冷媒通路孔１３６は、少なくとも一部が下吐出室凹部１６３Ｓに重なり、下吐出室凹部１６３Ｓと連通する位置に配置する。 Lower discharge chamber recess 163S includes a center _{O 1} of the sub bearing portion 161S, the midpoint _{O 4} of the line segment _{L 2} (length F) connecting the center _{O 2} and the center _{O 3} of below rivets 202S of the lower discharge holes 190S , a radial line L ₃ through the form in the sector ranging between radial line L ₄ open pitch angle 90 ° to the direction of the lower discharge holes 190S around the center O ₁ of the sub bearing portion 161S. The refrigerant passage hole 136 is disposed at a position where at least a part thereof overlaps with the lower discharge chamber recess 163S and communicates with the lower discharge chamber recess 163S.

図５に示すように、下吐出孔１９０Ｓの開口部周縁には、下吐出室凹部１６３Ｓの底部に対して盛り上がった環状の下弁座１９１Ｓが形成され、下弁座１９１Ｓが下吐出弁２００Ｓの前部と当接する。下吐出室凹部１６３Ｓの下弁座１９１Ｓまでの深さＨは、下吐出孔１９０Ｓの直径φＤ１の１．５倍以下とする。 As shown in FIG. 5, an annular lower valve seat 191 S that is raised with respect to the bottom of the lower discharge chamber recess 163 S is formed at the periphery of the opening of the lower discharge hole 190 S, and the lower valve seat 191 S is the lower discharge valve 200 S. Abuts the front. The depth H to the lower valve seat 191S of the lower discharge chamber recess 163S is 1.5 times or less the diameter φD1 of the lower discharge hole 190S.

下吐出孔１９０Ｓから冷媒が吐出するときの下吐出弁２００Ｓの開度すなわち下弁座１９１Ｓに対する下吐出弁２００Ｓのリフト量は、吐出流れの抵抗にならないリフト量とする必要がある。したがって、下吐出室凹部１６３Ｓの下弁座１６０Ｓまでの深さＨは、下吐出弁２００Ｓのリフト量と、下吐出弁２００Ｓ及び下吐出弁押さえ２０１Ｓの厚さを考慮して決定する必要があるが、下吐出孔１９０Ｓの直径φＤ１の１．５倍で充分である。 The opening degree of the lower discharge valve 200S when the refrigerant is discharged from the lower discharge hole 190S, that is, the lift amount of the lower discharge valve 200S with respect to the lower valve seat 191S needs to be a lift amount that does not become the resistance of the discharge flow. Therefore, the depth H to the lower valve seat 160S of the lower discharge chamber recess 163S needs to be determined in consideration of the lift amount of the lower discharge valve 200S and the thicknesses of the lower discharge valve 200S and the lower discharge valve presser 201S. However, 1.5 times the diameter φD1 of the lower discharge hole 190S is sufficient.

冷媒通路孔１３６は、少なくとも一部が上吐出室凹部１６３Ｔに重なって上吐出室凹部１６３Ｔと連通する位置に配置されている。上端板１６０Ｔに形成された上吐出室凹部１６３Ｔ及び上吐出弁収容凹部１６４Ｔについては、詳細な図示を省略するが、下端板１６０Ｓに形成された下吐出室凹部１６３Ｓ及び下吐出弁収容凹部１６４Ｓと同様の形状に形成されている。上端板カバー室１８０Ｔは、上端板カバー１７０Ｔのドーム状の膨出部と上吐出室凹部１６３Ｔと上吐出弁収容凹部１６４Ｔとにより構成される。 The refrigerant passage hole 136 is disposed at a position where at least a part thereof overlaps with the upper discharge chamber recess 163T and communicates with the upper discharge chamber recess 163T. The upper discharge chamber recess 163T and the upper discharge valve accommodating recess 164T formed in the upper end plate 160T are not shown in detail, but the lower discharge chamber recess 163S and the lower discharge valve accommodating recess 164S formed in the lower end plate 160S, It is formed in the same shape. The upper end plate cover chamber 180T is constituted by a dome-shaped bulged portion of the upper end plate cover 170T, an upper discharge chamber recess 163T, and an upper discharge valve housing recess 164T.

以上説明した実施例１のロータリ圧縮機１の構成により、下吐出孔１９０Ｓと冷媒通路孔１３６の入口との間の距離を短くすることができる。よって、下端板カバー室１８０Ｓの容積、すなわち、下吐出室凹部１６３Ｓの容積と下吐出弁収容凹部１６４Ｓの容積の和の容積を、従来に比較して大幅に小さくすることができる。これにより、上シリンダ１２１Ｔで圧縮されて上吐出孔１９０Ｔから吐出された冷媒が、冷媒通路孔１３６を逆流して下端板カバー室１８０Ｓに流れ込む流量を小さくすることができ、ロータリ圧縮機１の効率低下を防ぐことができる。 With the configuration of the rotary compressor 1 according to the first embodiment described above, the distance between the lower discharge hole 190S and the inlet of the refrigerant passage hole 136 can be shortened. Therefore, the volume of the lower end plate cover chamber 180S, that is, the sum of the volume of the lower discharge chamber recess 163S and the volume of the lower discharge valve housing recess 164S can be significantly reduced as compared with the conventional case. As a result, the refrigerant compressed by the upper cylinder 121T and discharged from the upper discharge hole 190T can flow back into the lower end plate cover chamber 180S through the refrigerant passage hole 136, thereby reducing the efficiency of the rotary compressor 1. Decline can be prevented.

図６は、実施例２のロータリ圧縮機の下吐出弁を取付けた下吐出弁収容凹部を示す縦断面図である。図６に示すように、実施例２のロータリ圧縮機１では、下端板１６０Ｓ２に形成された下吐出室凹部１６３Ｓ２及び下吐出弁収容凹部１６４Ｓ２の下弁座１９１Ｓまでの深さＨ_２は、実施例１のロータリ圧縮機１の下端板１６０Ｓに形成された下吐出室凹部１６３Ｓ及び下吐出弁収容凹部１６４Ｓの下弁座１９１Ｓまでの深さＨに比較して浅くしている。下端板カバー１７０Ｓ２は、下吐出弁押さえ２０１Ｓの前部と対向する部分に凹部１７１Ｓ２を有し、下吐出弁押さえ２０１Ｓの前部が下吐出室凹部１６３Ｓ２から突出する部分を収容している。凹部１７１Ｓ２から下弁座１９１Ｓまでの深さは、下吐出孔１９０Ｓの直径φＤ１の１．５倍以下に形成されている。 FIG. 6 is a longitudinal cross-sectional view showing a lower discharge valve housing recess in which the lower discharge valve of the rotary compressor of the second embodiment is attached. As shown in FIG. 6, in the rotary compressor 1 of the second embodiment, the depth H ₂ to the lower valve seat 191S of the lower discharge chamber recess 163S2 and the lower discharge valve housing recess 164S2 formed in the lower end plate 160S2 is It is made shallow compared with the depth H to the lower valve seat 191S of the lower discharge chamber recessed part 163S and the lower discharge valve accommodation recessed part 164S formed in the lower end plate 160S of the rotary compressor 1 of Example 1. The lower end plate cover 170S2 has a recess 171S2 at a portion facing the front portion of the lower discharge valve retainer 201S, and accommodates a portion where the front portion of the lower discharge valve retainer 201S protrudes from the lower discharge chamber recess 163S2. The depth from the recess 171S2 to the lower valve seat 191S is formed to be 1.5 times or less the diameter φD1 of the lower discharge hole 190S.

以上説明した実施例２のロータリ圧縮機１の構成により、実施例１のロータリ圧縮機１よりも下吐出弁収容凹部１６４Ｓ２の容積を小さくすることができ、これにより、上シリンダ１２１Ｔで圧縮されて上吐出孔１９０Ｔから吐出された冷媒が、冷媒通路孔１３６を逆流して下端板カバー室１８０Ｓ２に流れ込む流量をさらに小さくすることができ、ロータリ圧縮機１の効率低下を防ぐことができる。 Due to the configuration of the rotary compressor 1 of the second embodiment described above, the volume of the lower discharge valve accommodating recess 164S2 can be made smaller than that of the rotary compressor 1 of the first embodiment, and thus the compressed by the upper cylinder 121T. The flow rate of the refrigerant discharged from the upper discharge hole 190T backflowing through the refrigerant passage hole 136 and flowing into the lower end plate cover chamber 180S2 can be further reduced, and a reduction in the efficiency of the rotary compressor 1 can be prevented.

図７は、実施例３のロータリ圧縮機の下吐出弁を取付けた下吐出弁収容凹部を示す縦断面図である。図７に示すように、実施例３のロータリ圧縮機１では、下吐出弁押さえ２０１Ｓ３の前端部は、下端板カバー１７０Ｓと近接する部分の厚さが他の部分の厚さよりも薄く形成されている。これにより、実施例１のロータリ圧縮機１の下吐出弁２０１Ｓと同じ開度を確保しながら下吐出室凹部１６３Ｓ３及び下吐出弁収容凹部１６４Ｓ３の下弁座１９１Ｓまでの深さＨ２を実施例２と同様に浅くしている。 FIG. 7 is a longitudinal cross-sectional view showing a lower discharge valve accommodating recess to which a lower discharge valve of the rotary compressor of the third embodiment is attached. As shown in FIG. 7, in the rotary compressor 1 according to the third embodiment, the front end portion of the lower discharge valve presser 201S3 is formed so that the thickness of the portion adjacent to the lower end plate cover 170S is thinner than the thickness of the other portions. Yes. Thus, the depth H2 to the lower valve seat 191S of the lower discharge chamber recess 163S3 and the lower discharge valve housing recess 164S3 is secured while securing the same opening as the lower discharge valve 201S of the rotary compressor 1 of the first embodiment. Like shallow.

以上説明した実施例３のロータリ圧縮機１の構成により、実施例２のロータリ圧縮機１よりも、実施例２の凹部１７１Ｓ２の容積の分だけ、下端板カバー室１８０Ｓ３の容積を小さくすることができ、これにより、上シリンダ１２１Ｔで圧縮されて上吐出孔１９０Ｔから吐出された冷媒が、冷媒通路孔１３６を逆流して下端板カバー室１８０Ｓ３に流れ込む流量をさらに小さくすることができ、ロータリ圧縮機１の効率低下を防ぐことができる。 With the configuration of the rotary compressor 1 of the third embodiment described above, the volume of the lower end plate cover chamber 180S3 can be made smaller than the rotary compressor 1 of the second embodiment by the volume of the recess 171S2 of the second embodiment. Thus, the refrigerant compressed by the upper cylinder 121T and discharged from the upper discharge hole 190T can flow back into the lower end plate cover chamber 180S3 through the refrigerant passage hole 136, thereby further reducing the rotary compressor. 1 can be prevented.

図８は、実施例４のロータリ圧縮機の下端板を示す下面図である。図８に示すように、実施例４のロータリ圧縮機１では、下端板１６０Ｓ４（及び、下シリンダ１２１Ｓ、中間仕切板１４０、上シリンダ１２１Ｔ、上端板１６０Ｔ）に設けられた冷媒通路孔１３６Ｎは、実施例１のロータリ圧縮機１の冷媒通路孔１３６よりも小径とされ、２本設けられている（３本以上としてもよい）。２本（又は３本以上）の冷媒通路孔１３６Ｎの合計断面積は、実施例１のロータリ圧縮機１の冷媒通路孔１３６の断面積と同等とする。これにより、副軸受部１６１Ｓの中心Ｏ_１から冷媒通路孔１３６Ｎの最外周までの半径Ｒ１を、図４に示す実施例１のロータリ圧縮機１の副軸受部１６１Ｓの中心Ｏ_１から冷媒通路孔１３６の最外周までの半径Ｒ１よりも小さくすることができ、円形の下吐出室凹部１６３Ｓ４の径を小さくすることができる。 FIG. 8 is a bottom view showing a lower end plate of the rotary compressor of the fourth embodiment. As shown in FIG. 8, in the rotary compressor 1 of the fourth embodiment, the refrigerant passage hole 136N provided in the lower end plate 160S4 (and the lower cylinder 121S, the intermediate partition plate 140, the upper cylinder 121T, and the upper end plate 160T) The diameter is smaller than the refrigerant passage hole 136 of the rotary compressor 1 of the first embodiment, and two are provided (may be three or more). The total cross-sectional area of the two (or three or more) refrigerant passage holes 136N is equal to the cross-sectional area of the refrigerant passage hole 136 of the rotary compressor 1 of the first embodiment. Accordingly, the radius R1 from the center _{O 1} of the sub bearing portion 161S to the outermost periphery of the refrigerant passage holes 136N, the refrigerant passage holes from the center _{O 1} of the sub bearing portion 161S of the rotary compressor 1 of the first embodiment shown in FIG. 4 The radius can be smaller than the radius R1 up to the outermost periphery of 136, and the diameter of the circular lower discharge chamber recess 163S4 can be reduced.

以上説明した実施例４のロータリ圧縮機１の構成により、実施例１のロータリ圧縮機１の下吐出室凹部１６３Ｓの底面積よりも下吐出室凹部１６３Ｓ４の底面積を小さくして下吐出室凹部１６３Ｓ４の容積を小さくすることができ、これにより、上シリンダ１２１Ｔで圧縮されて上吐出孔１９０Ｔから吐出された冷媒が、冷媒通路孔１３６Ｎを逆流して下端板カバー室１８０Ｓ４に流れ込む流量をさらに小さくすることができ、ロータリ圧縮機１の効率低下を防ぐことができる。 With the configuration of the rotary compressor 1 according to the fourth embodiment described above, the bottom area of the lower discharge chamber recess 163S4 is made smaller than the bottom area of the lower discharge chamber recess 163S of the rotary compressor 1 according to the first embodiment. The volume of 163S4 can be reduced, thereby further reducing the flow rate of the refrigerant compressed by the upper cylinder 121T and discharged from the upper discharge hole 190T backflowing the refrigerant passage hole 136N and flowing into the lower end plate cover chamber 180S4. It is possible to prevent the reduction in efficiency of the rotary compressor 1.

また、副軸受部１６１Ｓの中心Ｏ_１から冷媒通路孔１３６Ｎの最外周までの半径Ｒ１を、図４に示す実施例１のロータリ圧縮機１の副軸受部１６１Ｓの中心Ｏ_１から冷媒通路孔１３６の最外周までの半径Ｒ１よりも小さくすることができるので、下端板１６０Ｓ４（及び、下シリンダ１２１Ｓ、中間仕切板１４０、上シリンダ１２１Ｔ、上端板１６０Ｔ）の半径Ｒ２を、実施例１の下端板１６０Ｓ（及び、下シリンダ１２１Ｓ、中間仕切板１４０、上シリンダ１２１Ｔ、上端板１６０Ｔ）の半径Ｒ２（図４参照）より小さくすることができ、圧縮部１２の材料費の低減効果もある。 Moreover, the radius R1 from the center _{O 1} of the sub bearing portion 161S to the outermost periphery of the refrigerant passage holes 136N, the refrigerant passage from the center _{O 1} of the sub bearing portion 161S of the rotary compressor 1 of the first embodiment shown in FIG. 4 the hole 136 Since the radius R2 of the lower end plate 160S4 (and the lower cylinder 121S, the intermediate partition plate 140, the upper cylinder 121T, and the upper end plate 160T) can be made smaller than the radius R1 up to the outermost periphery of the lower end plate of the first embodiment. 160S (and the lower cylinder 121S, the intermediate partition plate 140, the upper cylinder 121T, and the upper end plate 160T) can be made smaller than the radius R2 (see FIG. 4), and the material cost of the compression unit 12 can be reduced.

図９は、実施例５のロータリ圧縮機の下端板を示す下面図である。図９に示すように、実施例５のロータリ圧縮機１では、下端板１６０Ｓ５（及び、下シリンダ１２１Ｓ、中間仕切板１４０、上シリンダ１２１Ｔ、上端板１６０Ｔ）に設けられた冷媒通路孔１３６Ｍは、実施例４のロータリ圧縮機１の冷媒通路孔１３６Ｎの直径よりも幅が小さい長孔とされ、断面積は同等とされている。冷媒通路孔（長孔）１３６Ｍは、下弁座１９１Ｓの周方向に沿うように形成されている。これにより、副軸受部１６１Ｓの中心Ｏ_１から冷媒通路孔１３６Ｍの最外周までの半径Ｒ１を、図８に示す実施例４のロータリ圧縮機１の副軸受部１６１Ｓの中心Ｏ_１から冷媒通路孔１３６Ｎの最外周までの半径Ｒ１よりも小さくすることができ、円形の下吐出室凹部１６３Ｓ５の径を小さくすることができる。 FIG. 9 is a bottom view of the lower end plate of the rotary compressor of the fifth embodiment. As shown in FIG. 9, in the rotary compressor 1 of the fifth embodiment, the refrigerant passage hole 136M provided in the lower end plate 160S5 (and the lower cylinder 121S, the intermediate partition plate 140, the upper cylinder 121T, and the upper end plate 160T) In the rotary compressor 1 of the fourth embodiment, the refrigerant passage hole 136N is a long hole whose width is smaller than the diameter, and the cross-sectional areas are equal. The refrigerant passage hole (long hole) 136M is formed along the circumferential direction of the lower valve seat 191S. Accordingly, the radius R1 from the center _{O 1} of the sub bearing portion 161S to the outermost periphery of the refrigerant passage holes 136M, the refrigerant passage holes from the center _{O 1} of the sub bearing portion 161S of the rotary compressor 1 of the fourth embodiment shown in FIG. 8 The radius can be smaller than the radius R1 up to the outermost periphery of 136N, and the diameter of the circular lower discharge chamber recess 163S5 can be reduced.

以上説明した実施例５のロータリ圧縮機１の構成により、実施例４のロータリ圧縮機１の下吐出室凹部１６３Ｓ４の底面積よりも下吐出室凹部１６３Ｓ５の底面積をさらに小さくして下吐出室凹部１６３Ｓ５の容積を小さくすることができ、これにより、上シリンダ１２１Ｔで圧縮されて上吐出孔１９０Ｔから吐出された冷媒が、冷媒通路孔１３６Ｍを逆流して下端板カバー室１８０Ｓ５に流れ込む流量をさらに小さくすることができ、ロータリ圧縮機１の効率低下を防ぐことができる。 With the configuration of the rotary compressor 1 of the fifth embodiment described above, the bottom area of the lower discharge chamber recess 163S5 is made smaller than the bottom area of the lower discharge chamber recess 163S4 of the rotary compressor 1 of the fourth embodiment. The volume of the concave portion 163S5 can be reduced, whereby the refrigerant compressed by the upper cylinder 121T and discharged from the upper discharge hole 190T further flows back into the lower end plate cover chamber 180S5 through the refrigerant passage hole 136M. Therefore, the efficiency of the rotary compressor 1 can be prevented from being reduced.

また、副軸受部１６１Ｓの中心Ｏ_１から冷媒通路孔１３６Ｍの最外周までの半径Ｒ１を、図８に示す実施例４のロータリ圧縮機１の副軸受部１６１Ｓの中心Ｏ_１から冷媒通路孔１３６Ｎの最外周までの半径Ｒ１よりも小さくすることができるので、下端板１６０Ｓ５（及び、下シリンダ１２１Ｓ、中間仕切板１４０、上シリンダ１２１Ｔ、上端板１６０Ｔ）の半径Ｒ２を、実施例４の下端板１６０Ｓ４（及び、下シリンダ１２１Ｓ、中間仕切板１４０、上シリンダ１２１Ｔ、上端板１６０Ｔ）の半径Ｒ２（図４参照）より小さくすることができ、圧縮部１２の材料費のさらなる低減効果がある。 Moreover, the radius R1 from the center _{O 1} of the sub bearing portion 161S to the outermost periphery of the refrigerant passage holes 136M, the refrigerant passage holes from the center _{O 1} of the sub bearing portion 161S of the rotary compressor 1 of the fourth embodiment shown in FIG. 8 136N The radius R2 of the lower end plate 160S5 (and the lower cylinder 121S, the intermediate partition plate 140, the upper cylinder 121T, and the upper end plate 160T) can be made smaller than the radius R1 up to the outermost periphery of the lower end plate of the fourth embodiment. 160S4 (and the lower cylinder 121S, the intermediate partition plate 140, the upper cylinder 121T, the upper end plate 160T) can be made smaller than the radius R2 (see FIG. 4), and the material cost of the compression unit 12 can be further reduced.

図１０は、実施例６のロータリ圧縮機の下端板を示す下方斜視図である。図１０に示すように、実施例６のロータリ圧縮機１では、下端板１６０Ｓ６の下面（実施例１の下端板カバー１７０Ｓとの当接面となる）の下吐出室凹部１６３Ｓ及び下吐出弁収容凹部１６４Ｓが形成された領域以外の領域には、複数のボルト孔１３７の内側に、副軸受部１６１Ｓを囲む深さ１ｍｍ以下の環状の溝である冷媒導入部１６５Ｓ６が形成されている。なお、冷媒導入部１６５Ｓ６となる環状の溝は、下端板１６０Ｓ６の下面の代わりに下端板カバー１７０Ｓの上面に形成してもよい。 FIG. 10 is a lower perspective view illustrating the lower end plate of the rotary compressor of the sixth embodiment. As shown in FIG. 10, in the rotary compressor 1 of the sixth embodiment, the lower discharge chamber recess 163S and the lower discharge valve housing of the lower surface of the lower end plate 160S6 (which is a contact surface with the lower end plate cover 170S of the first embodiment). In regions other than the region where the recess 164S is formed, a refrigerant introduction portion 165S6 that is an annular groove having a depth of 1 mm or less surrounding the auxiliary bearing portion 161S is formed inside the plurality of bolt holes 137. In addition, you may form the cyclic | annular groove | channel used as the refrigerant | coolant introducing | transducing part 165S6 in the upper surface of the lower end plate cover 170S instead of the lower surface of the lower end plate 160S6.

冷媒導入部１６５Ｓ６の一端は、下吐出室凹部１６３Ｓに連通し、他端は、下吐出弁収容凹部１６４Ｓに連通する（冷媒導入部１６５Ｓ６を、下吐出室凹部１６３Ｓ又は下吐出弁収容凹部１６４Ｓのいずれか１つのみに連通させてもよい）。冷媒導入部１６５Ｓ６が下吐出室凹部１６３Ｓ又は下吐出弁収容凹部１６４Ｓに連通することによって、下吐出孔１９０Ｓから吐出された高温高圧の冷媒が下吐出室凹部１６３Ｓ又は下吐出弁収容凹部１６４Ｓを通って冷媒導入部１６５Ｓ６に導かれる。 One end of the refrigerant introduction portion 165S6 communicates with the lower discharge chamber recess 163S, and the other end communicates with the lower discharge valve accommodation recess 164S (the refrigerant introduction portion 165S6 is connected to the lower discharge chamber recess 163S or the lower discharge valve accommodation recess 164S). You may communicate with only one of them). The refrigerant introduction portion 165S6 communicates with the lower discharge chamber recess 163S or the lower discharge valve housing recess 164S, so that the high-temperature and high-pressure refrigerant discharged from the lower discharge hole 190S passes through the lower discharge chamber recess 163S or the lower discharge valve housing recess 164S. Then, it is guided to the refrigerant introduction part 165S6.

高温高圧の冷媒が冷媒導入部１６５Ｓ６に導かれることにより、下端板カバー１７０Ｓが加熱され、空気調和機を長時間停止した状態から起動するときに、ロータリ圧縮機１の圧縮機筐体１０の下部に滞留する液冷媒１９（図１参照）を加熱して、できるだけ早く気化させ、長時間に亘り潤滑油１８の代わりに液冷媒１９を吸い上げて圧縮部１２の摺動部が損傷するのを防ぐことができる。上シリンダ１２１Ｔで圧縮された冷媒が、冷媒通路孔１３６を逆流する量を減らすため、冷媒導入部１６５Ｓ６の空間の容積は、液冷媒１９を気化させるために必要な加熱量を確保できる範囲で小さくすることが望ましく、よって冷媒導入部１６５Ｓ６の深さは、液冷媒１９を気化させるために必要な加熱量を確保できる範囲で浅くする。 When the high-temperature and high-pressure refrigerant is guided to the refrigerant introduction part 165S6, the lower end plate cover 170S is heated and the lower part of the compressor casing 10 of the rotary compressor 1 is started when the air conditioner is started from a state of being stopped for a long time. The liquid refrigerant 19 (see FIG. 1) staying in the chamber is heated and vaporized as soon as possible, and the liquid refrigerant 19 is sucked up instead of the lubricating oil 18 for a long time to prevent the sliding portion of the compression section 12 from being damaged. be able to. In order to reduce the amount of the refrigerant compressed in the upper cylinder 121T flowing back through the refrigerant passage hole 136, the volume of the space of the refrigerant introduction portion 165S6 is small within a range in which the heating amount necessary for vaporizing the liquid refrigerant 19 can be secured. Therefore, the depth of the refrigerant introduction part 165S6 is made shallow within a range in which a heating amount necessary for vaporizing the liquid refrigerant 19 can be secured.

図１１は、実施例７のロータリ圧縮機の下端板と下端板カバーとを重ねた状態を示す下面図である。図１１に示すように、実施例７のロータリ圧縮機１では、平板状の下端板カバー１７０Ｓ７に、実施例６の下端板１６０Ｓ６と下シリンダ１２１Ｓとを締結する補助ボルト１７６（図３参照）の頭が下端板カバー１７０Ｓ７に当たるのを避けるための補助ボルト逃げ孔１７１Ｓ７が２つ設けられている。補助ボルト逃げ孔１７１Ｓ７は、一部分が下端板１６０Ｓ６に形成された冷媒導入部１６５Ｓ６と重なって連通し、冷媒排出部１７２Ｓ７となっている。なお、補助ボルト逃げ孔１７１Ｓ７が冷媒導入部１６５Ｓ６と重ならない場合は、下端板カバー１７０Ｓ７（１７０Ｓ、１７０Ｓ２）に、別途、下吐出室凹部１６３Ｓ又は下吐出弁収容凹部１６４Ｓ又は冷媒導入部１６５Ｓ６に連通する小孔（図示せず）を設け、この小孔を冷媒排出部１７２Ｓ７とすればよい。 FIG. 11 is a bottom view illustrating a state in which the lower end plate and the lower end plate cover of the rotary compressor according to the seventh embodiment are overlapped. As shown in FIG. 11, in the rotary compressor 1 of the seventh embodiment, auxiliary bolts 176 (see FIG. 3) for fastening the lower end plate 160S6 of the sixth embodiment and the lower cylinder 121S to the flat bottom plate cover 170S7. Two auxiliary bolt escape holes 171S7 are provided to prevent the head from hitting the lower end plate cover 170S7. A part of the auxiliary bolt escape hole 171S7 overlaps and communicates with the refrigerant introduction part 165S6 formed in the lower end plate 160S6, and serves as a refrigerant discharge part 172S7. When the auxiliary bolt escape hole 171S7 does not overlap with the refrigerant introduction part 165S6, the lower discharge plate recess 170S7 (170S, 170S2) is separately communicated with the lower discharge chamber recess 163S, the lower discharge valve housing recess 164S, or the refrigerant introduction part 165S6. A small hole (not shown) is provided, and this small hole may be used as the refrigerant discharge portion 172S7.

冷媒排出部１７２Ｓ７は、冷媒通路孔１３６を通さずに、圧縮冷媒を直接、圧縮機筐体１０内に排出する。冷媒排出部１７２Ｓ７により、下端板１６０Ｓ６の下吐出室凹部１６３Ｓ及び下吐出弁収容凹部１６４Ｓに潤滑油１８が溜まり下吐出孔１９０Ｓが潤滑油１８に浸漬することによる効率低下や騒音の発生を防ぐことができる。また、冷媒排出部１７２Ｓ７を設けることにより、冷媒排出部１７２Ｓ７から排出された冷媒が、長時間停止した状態で圧縮機筐体１０の下部に滞留する液冷媒１９（図１参照）を加熱して、気化を促進する効果もある。 The refrigerant discharge unit 172S7 discharges the compressed refrigerant directly into the compressor housing 10 without passing through the refrigerant passage hole 136. The refrigerant discharge portion 172S7 prevents the lowering of the efficiency and noise caused by the lubricating oil 18 accumulating in the lower discharge chamber recess 163S and the lower discharge valve housing recess 164S of the lower end plate 160S6 and the lower discharge hole 190S being immersed in the lubricating oil 18. Can do. In addition, by providing the refrigerant discharge unit 172S7, the refrigerant discharged from the refrigerant discharge unit 172S7 heats the liquid refrigerant 19 (see FIG. 1) that stays in the lower portion of the compressor housing 10 while stopped for a long time. It also has the effect of promoting vaporization.

以上、実施例を説明したが、前述した内容により実施例が限定されるものではない。また、前述した構成要素には、当業者が容易に想定できるもの、実質的に同一のもの、いわゆる均等の範囲のものが含まれる。さらに、前述した構成要素は適宜組み合わせることが可能である。さらに、実施例の要旨を逸脱しない範囲で構成要素の種々の省略、置換及び変更のうち少なくとも１つを行うことができる。 Although the embodiments have been described above, the embodiments are not limited to the above-described contents. In addition, the above-described constituent elements include those that can be easily assumed by those skilled in the art, those that are substantially the same, and those in a so-called equivalent range. Furthermore, the above-described components can be appropriately combined. Furthermore, at least one of various omissions, substitutions, and changes of the components can be made without departing from the scope of the embodiments.

１ロータリ圧縮機
１０圧縮機筐体
１１モータ
１２圧縮部
１５回転軸
１８潤滑油
１９液冷媒
２５アキュムレータ
３１Ｔアキュムレータ上Ｌ字管
３１Ｓアキュムレータ下Ｌ字管
１０５上吸入管
１０４下吸入管
１０７吐出管
１１１ステータ
１１２ロータ
１１５隙間
１２１Ｔ上シリンダ
１２１Ｓ下シリンダ
１２４Ｔ上スプリング穴
１２４Ｓ下スプリング穴
１２５Ｔ上ピストン
１２５Ｓ下ピストン
１２６Ｔ上スプリング
１２６Ｓ下スプリング
１２７Ｔ上ベーン
１２７Ｓ下ベーン
１２８Ｔ上ベーン溝
１２８Ｓ下ベーン溝
１３０Ｔ上シリンダ室
１３０Ｓ下シリンダ室
１３１Ｔ上吸入室
１３１Ｓ下吸入室
１３３Ｔ上圧縮室
１３３Ｓ下圧縮室
１３５Ｔ上吸入孔
１３５Ｓ下吸入孔
１３６，１３６Ｎ，１３６Ｍ冷媒通路孔
１３７ボルト孔
１４０中間仕切板
１５１副軸部
１５２Ｔ上偏心部
１５２Ｓ下偏心部
１５３主軸部
１５５給油縦孔
１５６給油横孔
１５８給油羽根
１６０Ｔ上端板
１６０Ｓ，１６０Ｓ２，１６０Ｓ４，１６０Ｓ５，１６０Ｓ６下端板
１６１Ｔ主軸受部
１６１Ｓ副軸受部
１６３Ｔ上吐出室凹部
１６３Ｓ，１６３Ｓ２，１６３Ｓ３，１６３Ｓ４，１６３Ｓ５下吐出室凹部
１６４Ｔ上吐出弁収容凹部
１６４Ｓ，１６４Ｓ２，１６４Ｓ３下吐出弁収容凹部
１６５Ｓ６冷媒導入部
１６６Ｓ８冷媒排出部
１７０Ｔ上端板カバー
１７０Ｓ，１７０Ｓ２，１７０Ｓ７下端板カバー
１７１Ｓ２凹部
１７１Ｓ７補助ボルト逃げ孔
１７２Ｓ７冷媒排出部
１７２Ｔ上端板カバー吐出孔
１７４，１７５通しボルト
１７６補助ボルト
１８０Ｔ上端板カバー室
１８０Ｓ，１８０Ｓ２，１８０Ｓ３，１８０Ｓ４,１８０Ｓ５下端板カバー室
１９０Ｔ上吐出孔
１９０Ｓ下吐出孔
１９１Ｓ下弁座
２００Ｔ上吐出弁
２００Ｓ下吐出弁
２０１Ｔ上吐出弁押さえ
２０１Ｓ，２０１Ｓ３下吐出弁押さえ
２０２Ｔ上リベット
２０２Ｓ下リベット
３１０取付脚 DESCRIPTION OF SYMBOLS 1 Rotary compressor 10 Compressor housing | casing 11 Motor 12 Compression part 15 Rotating shaft 18 Lubricating oil 19 Liquid refrigerant 25 Accumulator 31T Accumulator upper L-shaped pipe 31S Accumulator lower L-shaped pipe 105 Upper suction pipe 104 Lower suction pipe 107 Discharge pipe 111 Stator 112 rotor 115 clearance 121T upper cylinder 121S lower cylinder 124T upper spring hole 124S lower spring hole 125T upper piston 125S lower piston 126T upper spring 126S lower spring 127T upper vane 127S lower vane 128T upper vane groove 128S lower vane groove 130T upper cylinder chamber 130S lower Cylinder chamber 131T Upper suction chamber 131S Lower suction chamber 133T Upper compression chamber 133S Lower compression chamber 135T Upper suction hole 135S Lower suction hole 136, 136N, 136M Cold Medium passage hole 137 Bolt hole 140 Intermediate partition plate 151 Secondary shaft portion 152T Upper eccentric portion 152S Lower eccentric portion 153 Main shaft portion 155 Oil supply vertical hole 156 Oil supply horizontal hole 158 Oil supply blade 160T Upper end plate 160S, 160S2, 160S4, 160S5, 160S6 Lower end plate 161T Main bearing portion 161S Sub bearing portion 163T Upper discharge chamber recess 163S, 163S2, 163S3, 163S4, 163S5 Lower discharge chamber recess 164T Upper discharge valve storage recess 164S, 164S2, 164S3 Lower discharge valve storage recess 165S6 Refrigerant inlet 166S8 Refrigerant discharger 170T Upper end plate cover 170S, 170S2, 170S7 Lower end plate cover 171S2 Recess 171S7 Auxiliary bolt escape hole 172S7 Refrigerant discharge part 172T Upper end plate cover discharge hole 174, 175 Through bolt 176 Auxiliary bolt G 180T Upper end plate cover chamber 180S, 180S2, 180S3, 180S4, 180S5 Lower end plate cover chamber 190T Upper discharge hole 190S Lower discharge hole 191S Lower valve seat 200T Upper discharge valve 200S Lower discharge valve 201T Upper discharge valve holder 201S, 201S3 Lower discharge valve Presser 202T Upper rivet 202S Lower rivet 310 Mounting leg

Claims

A vertically mounted cylindrical compressor housing that is provided with an upper suction pipe and a lower suction pipe that are provided with a discharge pipe that discharges the refrigerant at the upper part and that sucks refrigerant at the lower part of the side surface, and a side portion of the compressor case An accumulator fixed to the upper suction pipe and the lower suction pipe, a motor disposed in the compressor housing, a motor disposed in the compressor housing and disposed below the motor and driven by the motor. A compression section that sucks and compresses refrigerant from the accumulator through a pipe and a lower suction pipe and discharges the refrigerant from the discharge pipe;
The compression unit is
An annular upper cylinder and a lower cylinder;
An upper end plate closing the upper side of the upper cylinder and a lower end plate closing the lower side of the lower cylinder;
An intermediate partition plate disposed between the upper cylinder and the lower cylinder and closing the lower side of the upper cylinder and the upper side of the lower cylinder;
A rotating shaft supported by a main bearing portion provided on the upper end plate and an auxiliary bearing portion provided on the lower end plate and rotated by the motor;
An upper eccentric portion and a lower eccentric portion provided with a phase difference of 180 ° from each other on the rotating shaft;
An upper piston fitted into the upper eccentric portion and revolved along the inner peripheral surface of the upper cylinder to form an upper cylinder chamber in the upper cylinder;
A lower piston fitted into the lower eccentric part and revolving along the inner peripheral surface of the lower cylinder to form a lower cylinder chamber in the lower cylinder;
An upper vane that protrudes from the upper vane groove provided in the upper cylinder into the upper cylinder chamber and contacts the upper piston to divide the upper cylinder chamber into an upper suction chamber and an upper compression chamber;
A lower vane protruding from a lower vane groove provided in the lower cylinder into the lower cylinder chamber and contacting the lower piston to partition the lower cylinder chamber into a lower suction chamber and a lower compression chamber;
An upper end plate cover that covers the upper end plate and forms an upper end plate cover chamber between the upper end plate and has an upper end plate cover discharge hole that communicates the upper end plate cover chamber and the inside of the compressor housing;
A lower end plate cover that covers the lower end plate and forms a lower end plate cover chamber with the lower end plate;
An upper discharge hole provided in the upper end plate for communicating the upper compression chamber and the upper end plate cover chamber;
A lower discharge hole provided in the lower end plate for communicating the lower compression chamber and the lower end plate cover chamber;
A refrigerant passage hole penetrating the lower end plate, the lower cylinder, the intermediate partition plate, the upper end plate, and the upper cylinder and communicating the lower end plate cover chamber and the upper end plate cover chamber;
A rotary compressor comprising:
An upper discharge valve housing recess provided in the upper end plate and extending in a groove shape from the position of the upper discharge hole;
A lower discharge valve housing recess provided in the lower end plate and extending in a groove shape from the position of the lower discharge hole;
A reed valve type upper discharge valve whose rear end portion is fixed in the upper discharge valve housing recess by an upper rivet and whose front portion opens and closes the upper discharge hole, and a rear end portion overlaps the upper discharge valve, and the upper discharge An upper discharge valve presser that is fixed by the upper rivet in the valve housing recess and the front part is warped to regulate the opening of the upper discharge valve;
A reed valve type lower discharge valve whose rear end is fixed in the lower discharge valve housing recess by a lower rivet and whose front part opens and closes the lower discharge hole and the rear end overlaps the lower discharge valve and the lower discharge A lower discharge valve holder which is fixed by the lower rivet in the valve housing recess and the front part is warped to regulate the opening of the lower discharge valve and is housed in the lower discharge valve housing recess;
With
The lower end plate cover is formed in a flat plate shape,
A lower discharge chamber recess is formed on the lower end plate so as to overlap the lower discharge hole side of the lower discharge valve housing recess, and the lower discharge chamber recess has a center of the sub-bearing portion and the lower discharge hole. A first diameter line passing through the center and the midpoint of the line segment connecting the centers of the lower rivets, and a second diameter line opened at a pitch angle of 90 ° about the center of the auxiliary bearing portion in the direction of the lower discharge hole Is formed within the fan-shaped range between
The lower end plate cover chamber is constituted by the lower discharge chamber recess and the lower discharge valve housing recess,
The refrigerant passage hole is disposed in communication with the lower discharge chamber recess at a position on the outer peripheral side of the lower end plate with respect to the lower discharge hole and at a position inside the inner peripheral wall of the lower discharge chamber recess. A rotary compressor characterized by that.

The rotary compressor according to claim 1, wherein the refrigerant passage hole is disposed in contact with an inner peripheral wall of the lower discharge chamber recess.

The lower discharge seat has a lower valve seat that swells in an annular shape on the periphery of the lower discharge hole, and the depth of the lower discharge chamber recess to the lower valve seat is formed to be 1.5 times or less the diameter φD1 of the lower discharge hole. The rotary compressor according to claim 1, wherein the rotary compressor is provided.

The lower discharge plate has a lower valve seat that swells in an annular shape at the periphery of the lower discharge hole, and the lower end plate cover has a recess in a portion facing the front end of the lower discharge valve presser, from the recess to the lower valve seat The rotary compressor according to claim 1, wherein the depth of the rotary compressor is formed to be not more than 1.5 times the diameter φD1 of the lower discharge hole.

The front end portion of the lower discharge valve presser is formed such that the thickness of the portion adjacent to the lower end plate cover is thinner than the thickness of the other portion. The described rotary compressor.

The rotary compressor according to any one of claims 1 to 5, wherein the refrigerant passage hole includes a plurality of circular holes.

6. The rotary compressor according to claim 1, wherein the refrigerant passage hole is a long hole along a circumferential direction of the lower discharge hole.

In the lower end plate or the lower end plate cover, a refrigerant introduction portion communicating with the lower discharge chamber recess or the lower discharge valve housing recess is formed as an annular groove having a depth of 1 mm or less surrounding the auxiliary bearing portion of the lower end plate. The rotary compressor according to any one of claims 1 to 7, wherein the rotary compressor is provided.

The lower end plate cover is provided with a refrigerant discharge portion that directly communicates the lower discharge chamber recess or the lower discharge valve housing recess or the refrigerant introduction portion with the inside of the compressor case and discharges the refrigerant into the compressor case. The rotary compressor according to claim 8, wherein the rotary compressor is provided.